Hybrid magnetic refrigerator

ABSTRACT

A compact and highly efficient hybrid magnetic refrigerator includes a hybrid refrigerating apparatus wherein an evaporator of a vapor compression refrigeration cycle and a heat exchanger of a magnetic refrigeration cycle are thermally connected. The magnetic refrigeration cycle is provided with a magnetic refrigeration unit in which a magnetic substance dissipates and absorbs heat according to the increase and decrease of a magnetic field in order to heat and cool a refrigerant circulating in its vicinity. The heated refrigerant is cooled by the evaporator of the vapor compression refrigeration cycle and the cooled refrigerant is supplied to the heat exchanger cooling the outside air.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is based upon and claims the benefit of priority fromprior Japanese Patent Application No. 2006-095945, filed Mar. 30, 2006,the entire contents of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a compact size hybrid magneticrefrigerator.

2. Description of the Related Art

Conventionally, a vapor compression refrigeration cycle has beengenerally utilized for a refrigerating apparatus for domestic, householdand business use (refrigeration ability: around 0.1 to 1 kW). As is wellknown, this vapor compression refrigeration cycle is provided with acompressor to compress a refrigerant and an expansion valve to expandthe refrigerant. A condenser to dissipate heat from the refrigerant andan evaporator to absorb heat in the refrigerant are arranged in therefrigerant channel between the compressor and the expansion valve.Accordingly, in this vapor compression refrigeration cycle, therefrigerant supplied from the compressor dissipates heat at thecondenser. The refrigerant supplied from the condenser is expanded atthe expansion valve and is supplied to the evaporator where heat isabsorbed. The refrigerant is again supplied to the compressor and iscompressed. The characteristics of this vapor compression refrigerationcycle are given as a temperature-entropy diagram (T-s diagram) and acompression-enthalpy diagram (p-h diagram), and a reversible cycle isexplained in both diagrams.

In addition, for special purposes limited to very low temperatureenvironments, JP-A 2002-106999 discloses a magnetic refrigeration cycleutilizing a magnetic substance (so-called magnetic working material),which has an exothermic and endothermic effect according to the increaseand decrease of a magnetic field. This magnetic refrigeration cycle isarranged with a superconducting magnet which applies a magnetic field inthe refrigerant channel path between the heat exchangers, and a magneticworking material having magneto-caloric effect is taken in and out inthis magnetic field. Accordingly, in this magnetic refrigeration cycle,by the operation of applying or eliminating a magnetic field to themagnetic working material, exothermic heat and endotherm from themagnetic working material are given to the refrigerant in therefrigerant channel path. The cooled refrigerant is supplied to aradiator, and the refrigerant given heat is supplied to an exhaust heatexchanger. The magnetic working material is not limited to a materialthat generates heat by the application of magnetic field and absorbsheat when a magnetic field is eliminated, but is known as a materialthat absorbs heat when a magnetic field is applied and generates heatwhen a magnetic field is eliminated.

In recent years, demands for a refrigerating apparatus which is able torefrigerate down to a low temperature region (−30 degrees Celsius orlower), such as to preserve freshness of food products using quickfreezing (−30 degrees Celsius or lower), is increasing for domestic,household and business use. However, conventionally, in order to realizea low temperature region (−30 degrees Celsius) for a vapor compressionrefrigeration cycle used generally in, such as, households, it isrequired to increase its compression ratio. By responding to suchdemand, a lubricant or coefficient of performance (COP) inside therefrigerating apparatus may deteriorate. Generally, a multistagecompression and single stage expansion refrigerating cycle is employedas measures to prevent such occurrence. However, such measures are saidto be unsuitable for domestic and household use due to the complexity ofrefrigerating system and the high-cost of such apparatus.

On the other hand, the magnetic refrigeration cycle requires anextremely large increase and decrease of the magnetic field in order togenerate a large difference in temperature in a magnetic refrigerationcycle using a magnetic substance having a known magneto-caloric effect.Accordingly, quite an ambitious and sophisticated apparatus likewise asuperconducting magnet is required. In a low magnetic field, which canbe realized by a permanent magnet, a magnetic substance being able togenerate a large temperature difference is already developed, and amagnetic refrigeration cycle using such magnetic substance has beendisclosed in JP-A 2002-106999 (KOKAI).

BRIEF SUMMARY OF THE INVENTION

According to an aspect of the present invention, there is provided ahybrid refrigerating apparatus comprising a vapor compressionrefrigeration cycle device in which a first refrigerant is circulatedand a magnetic refrigeration cycle device in which a second refrigerantis circulated,

the vapor compression refrigeration cycle device comprising:

a compressor configured to compress the first refrigerant;

a condenser configured to condense the first refrigerant supplied fromthe compressor to dissipate heat from the first refrigerant;

an expansion valve configured to expand the first refrigerant suppliedfrom the condenser; and

an evaporator configured to evaporate the first refrigerant suppliedfrom the expansion valve to absorb heat from the second refrigerant, thefirst refrigerant being supplied from the evaporator to the compressor;

the magnetic refrigeration cycle device comprising:

a pump configured to circulate the second refrigerant;

a magnetic refrigeration unit including a magnet device configured togenerate a magnetic field, a magnetic substance configured to dissipateor absorb heat in accordance with the increase and decrease of themagnetic field applied from the magnetic device, and a heat exchangestructure having an endothermic part in which the second refrigerant issupplied and the magnetic substance absorbs heat from the secondrefrigerant;

a first heat exchanger configured to exchange heat between the first andsecond refrigerants, to which the second refrigerant is supplied, thefirst heat exchanger being thermally connected to the evaporator of thevapor compression refrigeration cycle, and the second refrigerant in thefirst heat exchanger being cooled by the evaporator; and

a second heat exchanger configured to cool an atmosphere outside thesecond heat exchanger, the cooled second refrigerant being supplied tothe second heat exchanger.

Further, according to an aspect of the present invention, there isprovided a hybrid refrigerating apparatus comprising the vaporcompression refrigeration cycle device in which a first refrigerant iscirculated and a magnetic refrigeration cycle device in which a secondrefrigerant is circulated,

the vapor compression refrigeration cycle device comprising:

a first channel in which the first refrigerant is circulated;

a compressor, provided in the first channel, configured to compress afirst refrigerant;

an expansion valve, provided in the first channel, configured to expandthe first refrigerant;

a condenser configured to dissipate heat from the first refrigerant, thecondenser being provided in the channel between the compressor and theexpansion valve; and

an evaporator configured to absorb heat from outside and transfer heatto the first refrigerant, the evaporator being provided in the channelbetween the expansion valve and the compressor;

the magnetic refrigeration cycle device comprising:

a pump configured to circulate the second refrigerant;

a branch unit configured to divide the second refrigerant supplied fromthe pump into second and third refrigerant channels;

a merging unit configured to merge the second and third refrigerantchannels and return the second refrigerant through the second and thirdrefrigerant channels to the pump;

a magnetic refrigeration unit including a heat exchange structureprovided with endothermic and exothermic parts, a magnet deviceconfigured to apply magnetic field to either one of the endothermic partand the exothermic part, and a magnetic substance, which is shiftedbetween the endothermic part and the exothermic part, configured todissipate or absorb heat in accordance with the increase and decrease ofthe magnetic field applied from the magnetic device, the endothermicpart being arranged in the second refrigerant channel to cool the secondrefrigerant and the exothermic part being arranged in the thirdrefrigerant channel to heat the second refrigerant;

a first heat exchanger, configured to cool the second refrigerant, thefirst heat exchanger being provided in the second channel and thermallyconnected to the evaporator of the vapor refrigeration cycle, and theheated second refrigerant being supplied to the first heat exchanger;and

a second heat exchanger configured to cool atmosphere outside the secondheat exchanger, the second heat exchanger being provided in the firstchannel and the cooled second refrigerant being supplied to the secondheat exchanger.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

FIG. 1 is a block diagram schematically showing a hybrid magneticrefrigerator according to an embodiment of the present invention.

FIG. 2 is a perspective view schematically showing a magneticrefrigeration unit shown in FIG. 1.

FIG. 3 is a block diagram schematically showing a hybrid magneticrefrigerator according to another embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

There will be described a hybrid magnetic refrigerator according to anembodiment of the present invention with reference to the drawings.

FIG. 1 schematically shows the hybrid magnetic refrigerator according toa first embodiment of the present invention. The hybrid magneticrefrigerator shown in this FIG. 1 comprises a combination of a vaporcompression refrigeration cycle 1 and a magnetic refrigeration cycle 10.In other words, the hybrid magnetic refrigerator shown in FIG. 1 isprovided with a heat exchange connection 8, which thermally connects thevapor compression refrigeration cycle 1 and the magnetic refrigerationcycle 10. An evaporator 2 in the vapor compression refrigeration cycle 1and a high temperature side heat exchanger 11 in the magneticrefrigeration cycle 10 are thermally attached for heat exchange at thisheat exchange connection 8.

As shown in FIG. 1, the vapor compression refrigeration cycle 1comprises a compressor 3 to compress a refrigerant and an expansionvalve 5 to expand the refrigerant. A condenser 4 and the evaporator 2within the heat exchange connection 8 are connected in the refrigerantchannel between the compressor 3 and expansion valve 5. Accordingly, therefrigerant in the refrigeration cycle 1 is compressed at the compressor3, and this compressed refrigerant is supplied to the condenser 4 wherethe heat from the compressed refrigerant is diffused. The compressedrefrigerant is supplied from the condenser 4 to the expansion valve 5,where it is expanded and supplied to the evaporator 2. At the evaporator2, the expanded refrigerant absorbs heat from the high temperature sideheat exchanger 11 of the magnetic refrigeration cycle 10, which isthermally connected to the evaporator 2 of the vapor compressionrefrigeration cycle 1, so that the high temperature side heat exchanger11 is deprived of heat quantity. Here, the evaporator 2 of the vaporcompression refrigeration cycle 1 cools off the heat exchanger 11 of themagnetic refrigeration cycle 10 at approximately below 0 degreesCelsius, or preferably, in the range of 0 to −10 degrees Celsius.

The magnetic refrigeration cycle 10 is provided with a pump 14 to supplythe refrigerant into the heat exchange connection 8. The refrigerantcooled down at the heat exchange connection 8 is supplied to a heatexchanger 16 where the refrigerant is heat exchanged between theexternal environment in which this heat exchanger 16 is situated and iscirculated so that it is supplied to the pump 14 again. The heatexchange connection 8 is provided with the heat exchanger 11 and amagnetic refrigeration unit 12, which has an exothermic unit 12A andendothermic unit 12B. The heat exchanger 11 and the exothermic unit 12Aof the magnetic refrigeration unit 12 are arranged at the hightemperature side, and the heat exchanger 16 and the endothermic unit 12Bof the magnetic refrigeration unit 12 are arranged at the lowtemperature side of this magnetic refrigeration cycle 10. The magneticrefrigeration unit 12 is provided with a magnet device 18 to applymagnetic field to the exothermic unit 12A and is connected to anexternal actuator 22 so that a magnetic substance 20 having amagneto-caloric effect is movable between the exothermic unit 12A andthe endothermic unit 12B. This magnetic substance has a characteristic(magneto-caloric effect) of dissipating and absorbing heat depending onthe increase and decrease of the magnetic field. The magnetic substance20 moving between the exothermic unit 12A and the endothermic unit 12Bis arranged in a tubular housing as explained later and moves therein inpiston action. In the case where the magnetic substance 20 having apositive magnetic effect wherein the magnetic substance 20 dissipatesheat (heat dissipation) when applied a magnetic field and absorbs heat(cools down) upon demagnetization is incorporated in the magneticrefrigeration unit 12, the magnet device 18 is arranged on the hightemperature side of the magnetic refrigeration cycle 10 as shown inFIG. 1. In the case where the magnetic substance 20 possesses a negativemagnetic effect, the magnet device 18 is arranged on the low temperatureside of the magnetic refrigeration cycle 10. Here, as for the magneticsubstance 20 having a negative magnetic effect, the magnetic substance20 absorbs heat (cools down) when it is applied a magnetic field anddissipates heat (heat dissipation) upon demagnetization.

Meanwhile, in this magnetic refrigeration cycle 10, the magneticrefrigeration unit 12 is arranged on the high temperature side and thelow temperature side of the magnetic refrigeration cycle 10, and aninsulation structure is provided between the high temperature side andthe low temperature side of the magnetic refrigeration unit 12 in orderto prevent heat transfer between the two sides.

In the magnetic refrigeration cycle 10 shown in FIG. 1, the refrigerantsupplied from the pump 3 is cooled down to the temperature of theevaporator 2 at the heat exchanger 11, which is thermally connected tothe evaporator 2 of the vapor compression refrigeration cycle 1, and issupplied to the exothermic unit 12A of the magnetic refrigeration unit12. At the exothermic unit 12A of the magnetic refrigeration unit 12,the temperature of the refrigerant is subject to increase fromexothermic heat of the magnetic substance 20, however, maintains arelatively low temperature such as around 0 degrees Celsius due to beingcooled in advance by the heat exchanger 11. The refrigerant maintainedat a relatively low temperature is supplied to the endothermic unit 12Bof the magnetic refrigeration unit 12 by the pressure from the pump 14.At this endothermic unit 12B, the magnetic substance 20 deprives therefrigerant of heat, and the refrigerant is further cooled down to, forexample, −20 to −30 degrees Celsius. The sufficiently cooled refrigerantis supplied to the heat exchanger 16 on the low temperature side of themagnetic refrigeration cycle 10 and is returned again to the pump 14 viathis heat exchanger 16. At the heat exchanger 16 on the low temperatureside of the magnetic refrigeration cycle 10, its external environment iscooled by the supplied refrigerant.

The cooling temperature difference at each of the vapor compressionrefrigeration cycle 1 and the magnetic refrigeration cycle 10 shown inFIG. 1 is within the range of approximately 20 to 30 degrees Celsius,or, preferably, greater or equal to 30 degrees Celsius. Accordingly, ifit can be cooled down to approximately 0 degrees Celsius at the vaporcompression refrigeration cycle 1, the heat exchanger 16 of the magneticrefrigeration cycle 10 will be able to refrigerate its environmentaltemperature down to −30 degrees Celsius or lower.

FIG. 2 shows an example of the structure of the magnetic refrigerationunit 12 shown in FIG. 1. As shown in FIG. 1, at the connection 8, thepipe 42 where the evaporated cooling refrigerant is circulatedintersects with the pipe 44 where the magnetic cooling refrigerant iscirculated, thereby thermally connecting the evaporator 2 of the vaporcompression refrigeration cycle 1 and the heat exchanger 11 on the hightemperature side of the magnetic refrigeration cycle 10. In other words,the pipes 42 and 44 are arranged in embedded structure at the connection8. The pipe 44 for magnetic cooling refrigerant is horseshoe-shaped. Oneside of this horseshoe-shaped pipe 44 for magnetic cooling refrigerantcorresponds to a high temperature side pipe 44A of the magneticrefrigeration cycle 10 and the other side corresponds to a lowtemperature side pipe 44B of the magnetic refrigeration cycle 10. Atubular section 48 which slidably receives the magnetic substance 20 areso extended as to penetrate through the high temperature side pipe 44Aand the low temperature side pipe 44B, thereby forming an embeddedstructure between the pipes 44A and 44B and the tubular section 48.Outside this tubular section 48 is provided an actuator 22 toselectively shift the magnetic substance 20 between the high temperatureside pipe 44A and the low temperature side pipe 44B. In addition,permanent magnets 50 are arranged on both sides of the high temperatureside pipe 44A where the tubular section 48 is extended, and by thesepermanent magnets 50, a magnetic field can be applied to the magneticsubstance 20 inside the tubular section 48. Accordingly, the hightemperature side and the low temperature side of the tubular section 48,which is applied a magnetic field from the permanent magnet 50, isdetermined as the exothermic unit 12A and the endothermic unit 12B ofthe magnetic refrigeration unit 12.

In the structure of the magnetic refrigeration unit 12 shown in FIG. 2,the evaporated cooling refrigerant is circulated in the pipe 42 and themagnetic cooling refrigerant is circulated in the pipe 44, and themagnetic cooling refrigerant is refrigerated by the evaporated coolingrefrigerant at the connection 8. This cooled refrigerant is circulatedfrom the high temperature side pipe 44A to the low temperature side pipe44B. At the high temperature side pipe 44A, when the magnetic substance20 is shifted to the exothermic section 12A of the high temperature sideof the tubular section 48, the magnetic substance 20 is exothermic dueto the application of magnetic field and conducts heat exchange betweenthe magnetic cooling refrigerant. Along with the heat dissipation of themagnetic substance 20, the temperature of the magnetic coolingrefrigerant increases. However, since the magnetic cooling refrigerantis cooled in advance, the magnetic cooling refrigerant maintains arelatively low temperature while being circulated in the low temperatureside pipe 44B. When the magnetic substance 20 is shifted to theendothermic unit 12B of the low temperature side of the tubular section48, the magnetic substance 20 applies an endothermic effect to themagnetic cooling refrigerant. The sufficiently cooled magnetic coolingrefrigerant is supplied to the heat exchanger 16 via the low temperatureside pipe 44B.

In the structure shown in FIG. 2, the connection 8 is illustrated with apair of permanent magnets 50 arranged in two places, and a tubularsection 48 is arranged between the pair of permanent magnets 50.However, it is obvious that a plurality of connections 8 may beprovided, or a combination of a permanent magnet 50 and a tubularsection 48 may be arranged in a plurality of places so that a pluralityof endothermic units 12B are provided to the low temperature side pipe44B to further cool the magnetic cooling refrigerant to a lowertemperature. Alternatively, as is obvious from the arrangement in FIG.2, an electromagnet may be provided instead of the permanent magnet 50.Further, it is preferable that a heat insulation zone 24 is providedbetween the high temperature section and low temperature side pipes 44Aand 44B so that heat is not transferred to both sides.

Meanwhile, when the magnetic substance 20 has a negative magnetic effectinstead of the magnetic substance 20 having the positive magneticeffect, it is obvious that the permanent magnet 50 or the electromagnetis provided on the low temperature side pipe 44B. There is no constrainton the time cycle for applying or eliminating a magnetic field to themagnetic substance 20, therefore, it may be determined appropriately inaccordance with the cooling characteristics realized at the magneticrefrigeration cycle 10. Alternatively, without providing an independentactuator 22, the magnetic substance 20 may be shifted by utilizing thepiston of the compressor 3 used in the vapor compression refrigerationcycle or a mechanical movement of a cylinder or some kind of mechanicalmovement.

In the hybrid magnetic refrigerator shown in FIGS. 1 and 2,refrigeration in a lower temperature can be realized by cooling therefrigerant of the magnetic refrigeration cycle by the vapor compressionrefrigeration cycle and further by the magnetic refrigeration cycle. Incomparison to the case where similar refrigeration is realized by onlythe magnetic refrigeration cycle, because the refrigerant circulatinginside the magnetic refrigeration cycle is cooled in advance, themagnetic refrigerator can be made compact.

FIG. 3 schematically shows the hybrid magnetic refrigerator according toanother embodiment of the present invention. In FIG. 3, same symbolswill be given and explanations will be omitted for sections and devicesequivalent to those shown in FIG. 1.

In the vapor compression refrigeration cycle 1 in the hybrid magneticrefrigerator shown in FIG. 3, a receiver 6 to store a liquefiedrefrigerant is provided between the condenser 4 and the expansion valve5. In other words, the refrigerant is compressed and liquefied at thecompressor 3 and is temporary stored in the receiver 6 after heat isreleased from the liquefied refrigerant at the condenser 4. Theliquefied refrigerant is supplied to the expansion valve 5 from thisreceiver 6 and is expanded and vaporized. The vaporized refrigerant issupplied to the evaporator 2, where it deprives heat from the peripheryof the evaporator 2.

In the hybrid magnetic refrigerator shown in FIG. 3, the evaporator 2 ofthe vapor compression refrigeration cycle 1 and the heat exchanger 11 ofthe magnetic refrigeration cycle are provided in the connection 8. Theheat exchanger 11 of the magnetic refrigeration cycle is cooled by theevaporator 2 of the vapor compression refrigeration cycle 1.Furthermore, the heat exchanger 11 of this magnetic refrigeration cycleis provided on the high temperature side of the magnetic refrigerationcycle.

In the magnetic refrigeration cycle 30 shown in FIG. 3, the refrigerantfrom the pump 32 is divided into two refrigerant channels; one on thelow temperature side and the other on the high temperature side, at abranch section. Then, the refrigerant merges again at the mergingsection and returns to the pump 32. In the refrigerant channel on thelow temperature side, the endothermic unit 12B of the magneticrefrigeration unit 12 is provided. The refrigerant is supplied via thisendothermic section 12B to the heat exchanger 16, which deprives theexternal environment of heat, and is again returned to the pump 32.Meanwhile, in the refrigerant channel on the high temperature side, theexothermic unit 12A of the magnetic refrigeration unit 12 is provided.Heat is transferred to the refrigerant from the magnetic substance 20 atthe exothermic unit 12A. The refrigerant passed through the exothermicunit 12A is supplied to the heat exchanger 11 of the magneticrefrigeration cycle, is refrigerated by the evaporator 2 of the vaporcompression refrigeration cycle 1 and is returned in similar fashion tothe pump 32.

The magnetic refrigeration unit 12 shown in FIG. 3 does not have thepipe 44 for magnetic cooling refrigerant formed in a horse-shoe shape inthe structure shown in FIG. 2. However, it can be realized by arrangingthe high temperature side pipe 44A and the low temperature side pipe 44Bin parallel. In other words, the refrigerant from the pump 14 is splitand supplied to the high temperature side pipe 44A and low temperatureside pipe 44B respectively, are again merged and returned to the pump14. As shown in FIG. 3, likewise the magnetic refrigeration cycle shownin FIGS. 1 and 2, when the magnetic substance 20 having a positivemagnetic effect is combined in the magnetic refrigeration unit 12, themagnet device 18 is arranged on the high temperature side of themagnetic refrigeration cycle. However, when the magnetic substance 20possesses a negative magnetic effect, the magnet device 18 is arrangedon the low temperature side of the magnetic refrigeration cycle 10.

In the hybrid magnetic refrigerator shown in FIG. 3, refrigeration in alower temperature can be realized by cooling the refrigerant of themagnetic refrigeration cycle at the vapor compression refrigerationcycle and further at the magnetic refrigeration cycle. In comparison tothe case where similar refrigeration is realized by only the magneticrefrigeration cycle, because the refrigerant circulating inside themagnetic refrigeration cycle is cooled in advance, the magneticrefrigerator can be made compact.

As mentioned above, according to the present invention, a hybridmagnetic refrigerator which is compact, highly efficient, canrefrigerate down to a low temperature region and can be used forhousehold, domestic and business purposes is provided.

Additional advantages and modifications will readily occur to thoseskilled in the art. Therefore, the invention in its broader aspects isnot limited to the specific details and representative embodiments shownand described herein. Accordingly, various modifications may be madewithout departing from the spirit or scope of the general inventiveconcept as defined by the appended claims and their equivalents.

1. A hybrid refrigerating apparatus comprising a vapor compressionrefrigeration cycle device in which a first refrigerant is circulatedand a magnetic refrigeration cycle device in which a second refrigerantis circulated, the vapor compression refrigeration cycle devicecomprising: a compressor configured to compress the first refrigerant; acondenser configured to condense the first refrigerant supplied from thecompressor to dissipate heat from the first refrigerant; an expansionvalve configured to expand the first refrigerant supplied from thecondenser; and an evaporator configured to evaporate the firstrefrigerant supplied from the expansion valve to absorb heat from thesecond refrigerant, the first refrigerant being supplied from theevaporator to the compressor; the magnetic refrigeration cycle devicecomprising: a pump configured to circulate the second refrigerant; amagnetic refrigeration unit including a magnet device configured togenerate a magnetic field, a magnetic substance configured to dissipateor absorb heat in accordance with the increase and decrease of themagnetic field applied from the magnetic device, and a heat exchangestructure having an endothermic part in which the second refrigerant issupplied and the magnetic substance absorbs heat from the secondrefrigerant; a first heat exchanger configured to exchange heat betweenthe first and second refrigerants, to which the second refrigerant issupplied, the first heat exchanger being thermally connected to theevaporator of the vapor compression refrigeration cycle, and the secondrefrigerant in the first heat exchanger being cooled by the evaporator;and a second heat exchanger configured to cool an atmosphere outside thesecond heat exchanger, the cooled second refrigerant being supplied tothe second heat exchanger.
 2. The hybrid refrigerating apparatusaccording to claim 1, wherein the heat exchange structure have anexothermic part in which the second refrigerant is supplied and themagnetic substance dissipates heat into the second refrigerant.
 3. Thehybrid refrigerating apparatus according to claim 1, wherein the secondrefrigerant is supplied to the endothermic part after absorbing heat inthe evaporator.
 4. The hybrid refrigerating apparatus according to claim2, wherein the exothermic part is arranged so as to be close to thefirst heat exchanger
 5. The hybrid refrigerating apparatus according toclaim 4, wherein the exothermic part is arranged at an upstream side ofthe second refrigerant in respect to the first heat exchanger.
 6. Thehybrid refrigerating apparatus according to claim 2, wherein an heatinsulating unit is provided between the exothermic part and theendothermic part.
 7. The hybrid refrigerating apparatus according toclaim 1, wherein the heat exchange structure includes a first pipe inwhich the first refrigerant flows and a second pipe in which the secondrefrigerant flows, and the first and second pipes are embedded in theheat exchange structure to form the evaporator and the first heatexchanger.
 8. The hybrid refrigerating apparatus according to claim 7,wherein the second pipe is provided with a high-temperature side sectionin which the heated second refrigerant flows and a low-temperature sidesection in which the cooled second refrigerant flows, thehigh-temperature side section and the low-temperature side section arearranged in parallel, the heat exchange structure includes a tubularsection which is arranged in the heat exchange structure so as topenetrate the high-temperature side section and the low-temperature sidesection of the second pipe for the second refrigerant to form a thirdheat exchanger, and the magnetic substance is arranged inside thetubular section.
 9. The hybrid refrigerating apparatus according toclaim 1, further comprising an actuator configured to shift the magneticsubstance.
 10. The hybrid refrigerating apparatus according to claim 1,wherein the compressor includes a piston configured to shift themagnetic material.
 11. A hybrid refrigerating apparatus comprising thevapor compression refrigeration cycle device in which a firstrefrigerant is circulated and a magnetic refrigeration cycle device inwhich a second refrigerant is circulated, the vapor compressionrefrigeration cycle device comprising: a first channel in which thefirst refrigerant is circulated; a compressor, provided in the firstchannel, configured to compress a first refrigerant; an expansion valve,provided in the first channel, configured to expand the firstrefrigerant; a condenser configured to dissipate heat from the firstrefrigerant, the condenser being provided in the channel between thecompressor and the expansion valve; and an evaporator configured toabsorb heat from outside and transfer heat to the first refrigerant, theevaporator being provided in the channel between the expansion valve andthe compressor; the magnetic refrigeration cycle device comprising: apump configured to circulate the second refrigerant; a branch unitconfigured to divide the second refrigerant supplied from the pump intosecond and third refrigerant channels; a merging unit configured tomerge the second and third refrigerant channels and return the secondrefrigerant through the second and third refrigerant channels to thepump; a magnetic refrigeration unit including a heat exchange structureprovided with endothermic and exothermic parts, a magnet deviceconfigured to apply magnetic field to either one of the endothermic partand the exothermic part, and a magnetic substance, which is shiftedbetween the endothermic part and the exothermic part, configured todissipate or absorb heat in accordance with the increase and decrease ofthe magnetic field applied from the magnetic device, the endothermicpart being arranged in the second refrigerant channel to cool the secondrefrigerant and the exothermic part being arranged in the thirdrefrigerant channel to heat the second refrigerant; a first heatexchanger, configured to cool the second refrigerant, the first heatexchanger being provided in the second channel and thermally connectedto the evaporator of the vapor refrigeration cycle, and the heatedsecond refrigerant being supplied to the first heat exchanger; and asecond heat exchanger configured to cool atmosphere outside the secondheat exchanger, the second heat exchanger being provided in the firstchannel and the cooled second refrigerant being supplied to the secondheat exchanger.
 12. The hybrid refrigerating apparatus according toclaim 11, wherein the exothermic part is arranged so as to be close tothe first heat exchanger.
 13. The hybrid refrigerating apparatusaccording to claim 11, wherein the exothermic part is arranged at anupstream side of the second refrigerant in respect to the first heatexchanger.
 14. The hybrid refrigerating apparatus according to claim 11,wherein a heat insulating unit is provided between the exothermic partand the endothermic part.
 15. The hybrid refrigerating apparatusaccording to claim 11, further comprising an actuator configured toshift the magnetic substance.
 16. The hybrid refrigerating apparatusaccording to claim 11, wherein the compressor includes a pistonconfigured to shift the magnetic material.